Split discharge line with integrated muffler for a compressor

ABSTRACT

A discharge pipe for connecting a compressor with a condenser in a vapor-compression system comprises an intake segment, a muffler, a splitter segment and first and second discharge segments. The intake segment is configured to connect to a discharge port of the compressor and receive compressed refrigerant flow. The muffler is connected to the intake segment for attenuating pulsations within the compressed refrigerant flow. The splitter segment is connected to the muffler and configured to divide the compressed refrigerant flow into first and second branches. The first discharge segment connects to the splitter to receive the first branch and is configured to connect to the condenser at a first position. The second discharge segment connects to the splitter to receive the second branch and is configured to connect to the condenser at a second location

BACKGROUND

Typical refrigeration and air conditioning systems rely onvapor-compression cycles to transfer heat from one location to anotherfor the purposes of cooling or heating an enclosed space. Suchvapor-compression cycles comprise a compressor, a condenser, anexpansion device and an evaporator connected to form a closed-loopcircuit. Each component of the system is connected by a length of pipingthat conducts a working fluid, such as a refrigerant, through thecircuit. The compressor controls the flow of the fluid through thecircuit to adjust the amount of temperature control that takes place inthe space. Compressors rely on mechanical means, such as twin screws,reciprocating pistons or scrolls, for drawing in the fluid from anintake line, compressing the fluid, and expelling the fluid to adischarge line at a higher pressure to push fluid through the system.Thus, compressors only perform work on one small portion of the totalworking fluid in the system at a time, the size of which depends on thecapacity of each compressor.

In chiller systems, where the vapor-compression circuit is used tofacilitate cooling to various spaces within a building, multiple, largecapacity compressors are often used to provide sufficient volumetricflow of refrigerant through the system. One such large-capacity systemcomprises a stacked chiller system in which the condenser, evaporatorand compressor are stacked vertically one on top of the other. Often,due to manufacturing tolerances and variations of assembly, each chillersystem takes on slight variations in the distances between connectionpoints for each component. In particular, difficulties may arise inassembling compressor discharge lines between the compressor and thecondenser. Typical vapor-compression circuits include a single dischargeline connecting the compressor with the condenser. The difficulties inassembling such discharge lines are exacerbated by the need to includeother system components such as mufflers for damping discharge pulses,valves for servicing the chiller system, and other components.

Usually, the working fluid is discharged from the compressor in pulsesas each compressed portion of fluid is released from the mechanicalcompression means, thus producing a burst of wave energy that propagatesthroughout the vapor-compression system. The compression means aretypically turned by motors operating at speeds such that the wavepulsations are discharged at a high frequency. The pulsations not onlyproduce vibration of the compressor, but also produce noise that isamplified by the working matter and the compressor. Such vibration isundesirable as it wears components of the compressor and producesadditional noise as the compressor vibrates. The magnitude of thedischarge pulsations is also intensified in large capacity compressorapplications. Thus, compressors are typically fitted with mufflersdownstream of the discharge pulses of the compressor to attenuatepulsations of the refrigerant.

Also, typical compressors include oil systems that circulate lubricatingand cooling oil to the mechanical compression means within thecompressor, where the oil and refrigerant become entrained. It isnecessary to separate the oil from the refrigerant before therefrigerant enters the condenser to optimize heat exchange efficiency ofthe system. Thus, vapor-compression circuits are typically fitted withseparators positioned between the compressor and the condenser to filteroil from the refrigerant.

Conventional vapor-compression system designs fail to address thevarious performance requirements of compressor discharge flow, mufflerpositioning and separator intake flow, in a compact, convenient andinexpensive package that also permits minute adjustments necessary toassemble such system and accommodate geometric tolerancing limitationsand installation variations. There is, therefore, a need for an improvedsystem for connecting compressors with condensers in vapor-compressionsystems.

SUMMARY

The present invention is directed to a discharge pipe for connecting acompressor with a condenser in a vapor-compression system. The dischargepipe includes an intake segment, a muffler, a splitter segment and firstand second discharge segments. The intake segment is configured toconnect to a discharge port of the compressor and receive compressedrefrigerant flow. The muffler is connected to the intake segment forattenuating pulsations within the compressed refrigerant flow. Thesplitter segment is connected to the muffler and configured to dividethe compressed refrigerant flow into first and second branches. Thefirst discharge segment connects to the splitter to receive the firstbranch and is configured to connect to the condenser at a firstposition. The second discharge segment connects to the splitter toreceive the second branch and is configured to connect to the condenserat a second location.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a diagram of a vapor-compression system including a splitdischarge line having an integrated muffler in accordance with oneembodiment of the present invention.

FIG. 2 is a side elevational view of a stacked chiller system includinga split discharge line as shown in FIG. 1.

FIG. 3 is a perspective view of another embodiment of a split dischargeline in accordance with the present invention also including anintegrated muffler and flow control valves.

DETAILED DESCRIPTION

FIG. 1 shows a schematic of vapor-compression system 10 including splitdischarge line 12A, integrated muffler 14 and integrated valves 15A and15B. Vapor-compression system 10 includes compressor 16, condenser 18,expansion device 20 and evaporator 22. Compressor 16, condenser 18,expansion device 20 and evaporator 22 are connected in a series circuitusing conduit including compressor discharge piping 12A, compressorsuction piping 12B, condenser piping 12C and evaporator piping 12D.Vapor-compression system 10 also includes other components such aseconomizer 24 and oil distribution system 26. In one embodiment,vapor-compression system 10 comprises a water cooled “chiller” systemthat is used to provide cooled air to a plurality of spaces such aswithin a building. For example, evaporator 22 also includes manifolds28A and 28B that conduct a coolant, such as water or a refrigerant, froma “cooler” heat exchanger through evaporator 22. The cooler heatexchanger services one or more heat exchangers used to cool theplurality of spaces. Condenser 18 includes manifolds 29A and 29B thatcirculate water from a cooling tower through condenser 18. The coolingtower cools water that is used to transfer heat from the chiller system.

In the embodiment shown, compressor 16 is a rotary screw compressor thatcompresses a refrigerant, such as R-122, to provide heated, highpressure refrigerant to condenser 18 through discharge line 12A. Inother embodiments, compressor 16 includes other mechanical means forcompressing a working fluid, such as reciprocating pistons or orbitingscrolls. For any mechanical compression means, compressor 16 is providedwith a source of oil from oil distribution system 26 to provide coolingand lubrication to compressor 16. The oil is mixed with the refrigerantwithin compressor 16 and both are delivered to condenser 18 throughdischarge line 12A. Discharge line 12A includes muffler 14 forattenuating pulsations and vibration resulting from a pulsed dischargeof the refrigerant from compressor 16. The oil is filtered from therefrigerant within condenser 18 through oil separator 30 that collectsand returns the oil to compressor 16 via distribution system 26. Usingcooling water from the cooling tower provided through manifold 29B, therefrigerant cools and condenses to a saturated liquid having a slightlylower temperature at a high pressure within condenser 16, and rejectingheat to the water-based heat exchanger.

From condenser 18, the refrigerant is conducted through condenser piping12C to expansion device 20 whereby the refrigerant undergoes a flashevaporation process to lower the pressure and temperature and isconverted to two-phase refrigerant comprising gaseous and liquid phaserefrigerant. Under pressure from compressor 16, the refrigerantcontinues through evaporator piping 12D to evaporator 22 whereby therelative warmth of the coolant from the cooler heat exchange provided bymanifold 28B vaporizes the refrigerant into a saturated vapor phaserefrigerant. Under suction from compressor 16, the refrigerant returnsto compressor 16. As such, vapor-compression system 10 operates usingwell-known thermodynamic principles to transfer heat from evaporator 22to condenser 18.

For clarity, FIG. 1 schematically diagrams the assembly ofvapor-compression system 10. In practice, it is desirable to assemblesystem 10 compactly such that system 10 can be positioned within smallerspaces inside of, or close to, a building or some other confined place.As such, it becomes a design consideration in positioning and assemblingthe components of system 10, such as compressor 16, condenser 18 andevaporator 22. Compressor discharge line 12A of the present inventionfacilitates assembly of system 10 by providing compact and flexiblepiping for connecting compressor 16 to condenser 18, incorporatingmuffler 14 and service valves 15A and 15B in an easily assembled andeasily manufactured system.

FIG. 2 shows split discharge line 12A having integrated muffler 14 andintegrated valves 15A and 15B incorporated into a stacked chillersystem. The stacked chiller system includes compressor 16, condenser 18,expansion device 20 and evaporator 22, which are connected to formvapor-compression system 10 as shown schematically in FIG. 1. AlthoughFIG. 2 shows a single compressor chiller system, other embodiments ofthe invention may be incorporated into double or multiple compressorchiller systems. Refrigerant discharged from compressor 16 travelsthrough discharge piping 12A to condenser 18, through expansion device20 to evaporator 22, and back to compressor 16 through compressorsuction piping 12B. Additionally, as indicated by arrows, another fluid,such as water from a cooling tower, is circulated through condenser 18to cool the refrigerant before the refrigerant is passed to expander 20.Likewise, as indicated by arrows, a coolant, such as a refrigerant froma cooler heat exchanger, is circulated through evaporator 22 to dumpheat into the refrigerant before the refrigerant is passed back tocompressor 16. The stacked chiller system also includes oil distributionsystem 26 which returns oil separated from the compressed refrigerant byseparator 30 within condenser 18 to compressor 16 whereby it is used tolubricate the mechanical compression system within compressor 16.

Condenser 18 comprises a shell and tube heat exchanger in which shell 31is partially cut away in FIG. 2 to show tube bundle 32 and oil separator30. Evaporator 22 also comprises a shell and tube heat exchangerincluding shell 33. Oil separator 30 comprises a filtration system inwhich incoming refrigerant/oil mixture is collected at distal ends ofseparator 30 from the various branches of discharge line 12A anddirected toward the center or middle portion of separator 30 whereby themixture is passed through one or more separation medium screens. Thescreens have porosity large enough to permit refrigerant to passthrough, but small enough to prevent oil from passing through. Theseparated refrigerant flows down from separator 30 to interact with tubebundle 32, while the separated oil is collected by oil distributionsystem 26. In other embodiments, separator 30 operates with other typesof filtration systems.

Various configurations of the stacked chiller system have capacitiessuch that they are suitable for cooling large buildings or spaces. Assuch, the individual components of the vapor-compression system arelarge in size and heavy such that assembly varies slightly from onesystem to the next. In one embodiment of chiller system 10 in which thepresent invention is used, evaporator 22, condenser 18 and compressor 16are stacked in a vertical configuration such that one rests on top ofthe other using various hardware. In one embodiment, condenser 18 andevaporator 22 are stacked on top of each other using brackets 34A and34B. Brackets 34A and 34B include footings 35A and 35B to provide afoundation upon which the chiller system rests. Footings 35A and 35B aretypically welded to a floor, or some other anchor point, such that thechiller system is immobilized once installed. Brackets 34A and 34B arewelded to end caps of manifolds 28A, 28B, 29A and 29B to supportevaporator 22 rigidly above condenser 18. Compressor 16 is connected toevaporator 22 using various means such as welded and fastened bracketssuch that compressor 16 is supported above evaporator 22. Aftercondenser 18, evaporator 22 and compressor 18 are assembled, the variouspiping systems for the chiller system are installed, such as used ineconomizer 24 and oil distribution system 26. Also, compressor inletline 12B and compressor discharge line 12A are installed to connectcompressor 16 with condenser 18 and evaporator 22. In otherconfigurations, chiller systems are installed in side-by-side systems inwhich condenser 18 and evaporator 22 both rest on footings that supportthe system. Such side-by-side configurations are also assembled usingbrackets that join condenser 18 and evaporator 22. The variousembodiments of discharge line 12A described herein are suitable for usewith such side-by-side chiller configurations.

As such, various tolerance limits are accumulated as condenser 18,evaporator 22 and compressor 16 are assembled, and the exactthree-dimensional relationship between these components varies from onechiller system to another. For example, the welding process used tofasten footings 35A and 35B and brackets 34A and 34B produce slightvariations in the position of condenser 18 and evaporator 22.Furthermore, the exact position of various features of each componentvaries within the acceptable tolerance range for each component. Inparticular, the position of discharge port 36 of compressor 16 and inletports 37A and 37B of condenser 18 are located within a tolerance band asdefined by the final design specifications. Thus, due to variousmanufacturing and assembly factors, the three-dimensional vectorsbetween discharge port 36 and inlet port 37A, discharge port 36 andinlet port 37B, and inlet port 37A and inlet port 37B vary frominstallation to installation.

Overcoming the variations in these vectors and other benefits areachieved with the configuration and assembly of split discharge line 12Aof the present invention. Discharge pipe 12A also allows for integratingother components into the chiller system, such as muffler 14 and valves15A and 15B, in a compact manner. Typically, discharge line 12A extendsfrom condenser 18, to alongside evaporator 22 and up to compressor 16.In various embodiments of the invention, discharge line 12A includesvarious bends such that discharge pipe 12A bends around evaporator 22 toreach the inlet ports of condenser 18 and the discharge port ofcompressor 16. For example, in one embodiment, discharge pipe 12Aincludes a thirty degree bend to extend from alongside evaporator 22 toinlet ports 37A and 37B, which, in various embodiments, are positionedthirty degree from top-dead-center of condenser 18. Discharge pipe 12Aalso provides the added benefit of improving refrigerant flow into oilseparator 30. Specifically, discharge line 12A slows the velocity of therefrigerant as it enters separator 30 such that the separation mediumscreens are better able to filter oil from the refrigerant. As such,discharge pipe 12A provides a compact, efficient and easilymanufacturable system for conveying refrigerant from compressor 16 tocondenser 18.

FIG. 3 shows split discharge line 12A having integrated muffler 14 andintegrated flow control valves 15A and 15B. Discharge line 12A alsoincludes inlet elbow 38, T-joint 39, first split line 40A, second splitline 40B, first split elbow 42A, second split elbow 42B, first outletline 44A and second outlet line 44B.

Inlet elbow 36 is connected to discharge port 36 of compressor 16 withflange 46, which is typically bolted to compressor 16. In oneembodiment, inlet elbow 38 is fabricated from steel tubing such thatelbow 38 is rigidly connected with compressor 16 to provide a stableplatform for connecting with muffler 14. In various embodiments of theinvention, inlet elbow 38 has a large diameter compatible with thedischarge ports of high capacity compressors suitable for use in watercooled chiller systems. In various high-capacity embodiments of theinvention, elbow 38 has a diameter of 5 inches (˜12.7 cm) or 6 inches(˜15.24 cm). Inlet elbow 38 includes a ninety-degree bend and isoriented to direct compressed refrigerant flow perpendicular to thedirection of refrigerant flow within condenser 18. Inlet elbow 38extends the flow of compressed refrigerant from discharge port 36laterally from compressor 16 such that the flow of the compressedrefrigerant is extended to the side of compressor 16 above evaporator 22and condenser 18.

Muffler 14 is connected to the outlet end of elbow 38 and includes aninner flow path compatible for connecting with elbow 38. Muffler 14comprises any suitable muffler as is used in the industry and isconfigured to efficiently attenuate pulsation transmission in the pulseddischarges of the compressed refrigerant. In various embodiments,muffler 14 comprises a baffle type or sound absorbing type muffler, suchas a baffle tube or fiberglass disk style muffler. As depicted in FIG.3, muffler 14 includes eyelets or hooks which are used to facilitateinstallation of split discharge line 12A with a crane or some otherlifting device.

T-joint 39 is fluidly connected to the outlet end of muffler 14 andincludes inlet elbow 39A, splitter 39B and discharge portions 39C and39D. In other embodiments, the muffler may be disposed in otherconfigurations such as to eliminate the need for an inlet elbow 39A. Inone embodiment, T-joint 39 is comprised of steel such as that of elbow38. Typically, inlet elbow 39A has a diameter matching that of inletelbow 38 and the inner flow path of muffler 14 to minimize pressure lossin the flow of the compressed refrigerant, which increases efficiency ofvapor-compression system 10. As such, a continuous, generally constantcross section flow path is formed by elbow 38, muffler 14 and inletelbow 39A. In the embodiment of FIG. 3, inlet elbow 39A includes aninety-degree bend and directs the flow of compressed refrigerantparallel to the direction of refrigerant flow through condenser 18. Asshown in FIGS. 2 and 3, inlet elbow 39A is oriented with an outlet endthereof directed towards the condenser 22 to extend the flow ofcompressed refrigerant down from compressor 16 to alongside condenser22. Inlet elbow 39A leads into and is in fluid communication with aninlet of the “T” or splitter 39B.

Splitter 39B comprises a segment of tubing integral with elbow 39A thatis oriented generally perpendicular to the discharge end of inlet elbow39A. Splitter 39B produces a two-way, ninety-degree redirection in theflow of compressed refrigerant such that the refrigerant is againflowing perpendicular to flow of refrigerant within condenser 18. Themiddle portion of splitter 39B has a diameter matching that of elbow 38and elbow 39A to minimize pressure loss in the flow of compressedrefrigerant. The distal ends of splitter 39B are tapered, or neckeddown, to a diameter smaller than that of inlet elbow 38 and inlet elbow39A to form discharge portions 39C and 39D. The diameters of dischargeportions 39C and 39D are typically sized to match that of a diameter inwhich standard tubing is available in accordance with the desiredbalance of pressure drop for the system 10. For example, copper tubingis typically available in 3.125 inch (˜7.94 cm) diameter stock tubing.

First split line 40A and second split line 40B are connected todischarge portions 39C and 39D, of splitter 39B respectively. In oneembodiment, split lines 40A and 40B are comprised of stock copper tubingsegments sized to be received into discharge portions 39C and 39D,respectively. Split lines 40A and 40B extend generally horizontally todirect the flow of the compressed refrigerants out toward inlet ports37A and 37B of condenser 18. Split line 40A connects with valve 15A atits distal end. Likewise, split line 40B connects with valve 15B at itsdistal end. In one embodiment of the invention, valves 15A and 15Bcomprise stock ball valves as are commercially available. Valves 15A and15B provide a means for isolating components of the chiller system inorder to perform service or maintenance. For example, valves 15A and 15Bcan be shut to allow the separation medium screens within separator 30to be cleaned or replaced.

Elbows 42A and 42B connect with valves 15A and 15B, respectively. In theillustrated embodiment, elbows 42A and 42B include ninety degree bendsthat redirect the flow of the compressed refrigerant such that thecompressed refrigerant is flowing parallel to the direction ofrefrigerant flow within condenser 18. Outlet lines 44A and 44B connectto elbows 42A and 42B, respectively, to extend the flow of compressedrefrigerant from discharge port 36 of compressor 16 to inlet ports 37Aand 37B, respectively, of condenser 18. Outlet lines 44A and 44B caninclude slight bends such that outlet lines wrap around the curve ofshell 33 of evaporator 22 to enter inlet ports 37A and 37B. As shown inthe embodiment of FIGS. 2 and 3 embodiment, top portions of outlet lines44A and 44B slope slightly away from evaporator 22, while bottomportions of outlet lines 44A and 44B slope slightly toward evaporator 22with respect to the downward flow of the compressed refrigerant. In oneembodiment of the invention, outlet lines 44A and 44B include thirtydegree bends, but other angles of bends may used in other embodiments toaccommodate extension from discharge port 36 to inlet ports 37A and 37B,depending on, for example, the specific compressor used. Such bends maybe in the range of approximately ten to approximately fifty degrees. Assuch, split discharge line 12A remains closely situated near compressor16, evaporator 22 and condenser 18 such the overall width of the chillersystem is not expanded and remains in a compact configuration. Outletlines 44A and 44B are manufactured from stock sized copper tubing havinga diameter matching that of split lines 40A and 40B.

The outlet ends of outlet lines 44A and 44B extend far enough tocomplete the connection of discharge port 36 with inlet ports 37A and37B, extending into shell 31 of condenser 18 to join with oil separator28. In other embodiments of the invention, valves 15A and 15B can bepositioned at the discharge ends of outlet lines 44A and 44B, wherebyconnection to inlet ports 37A and 37B can be completed with additionalsegments of piping. Split line 40A, valve 15A, elbow 42A and outlet line44A extend from discharge port 36 to inlet port 37A. Likewise, splitline 40B valve 15B, elbow 42B and outlet line 44B extend from dischargeport 36 to inlet port 37B. As such, split discharge line 12A provides asystem for connecting discharge port 36 with inlet ports 37A and 37B,while providing a platform for muffler 14 and valves 15A and 15B, whichaccommodates manufacturing and assembly variations in stacked chillersystems. Specifically, the various connection points and materialproperties, among other things, allow split discharge line 12A toaccommodate variations in geometric tolerance limits within the chillersystem.

As discussed above, the three-dimensional vectors between discharge port36 and inlet ports 37A and 37B change after a chiller system isassembled. The individual tolerances for each components, such asbrackets 34A and 35A, combine with variations that arise duringassembly, such as welding of footings 35A and 35B, to change thedistance between these openings, requiring split discharge line 12A tohave variability in assembly and installation. For example, if splitdischarge line 12A were comprised of a single, steel discharge pipe, itwould be difficult or impossible to connect vertical portions 44A and44B with inlet ports 37A and 37B if the position of discharge port 36,with respect to inlet ports 37A and 37B, were out of spec due toaccumulation of tolerances or assembly variations. Thus, in the presentinvention, the split discharge pipe is divided into smaller segmentssuch that accumulated tolerances or assembly variations can beaccommodated by discharge line 12A. The present invention, however, alsostrategically divides discharge line 12A so that other systemcomponents, such as muffler 14 and valves 15A and 15B, can beincorporated into discharge line 12A in a compact manner.

In one embodiment, elbow 38 and T-joint 39 are comprised of steel suchthat they are rigidly connected with compressor 16 and muffler 14. Inone embodiment of the invention, split lines 40A and 40B and outletlines 44A and 44B are manufactured of stock sized copper tubing. Copperis more easily bent than steel such that the distal ends of outlet lines44A and 44B can be slightly adjusted for insertion into inlets 37A and37B without producing excessive stress on outlet lines 44A and 44B.Furthermore, the distal ends of outlet lines 44A and 44B can be adjustedby rotating the various tube components at their juncture points withadjoining components. For example, T-joint 39 can be rotated in muffler14 to raise and lower split lines 40A and 40B with respect to condenser18, and split lines 40A and 40B can be rotated in discharge portions 39Cand 39D of T-joint 39 to adjust the horizontal positions of verticallines 44A and 44B with respect to condenser 18. Additionally, elbows 42Aand 42B and discharge lines 40A and 40B provide an additional means forindividually adjusting the position of outlet lines 44A and 44B. Inother embodiments, elbow 38 can be rotated in muffler 14 to accommodatedesign and assembly variations. For example, elbow 38 can be rotated todirect refrigerant flow in a direction parallel to the direction elbow39A of T-joint 39 directs flow, such as for use in side-by-side chillersystem configurations of split discharge line 12A. After split dischargeline 12A is installed into a chiller system, the individual joints canbe brazed together to lock discharge line 12A in place. Alternatively,other types of fastening means can be utilized. Inlet elbow 39 ofT-joint 39 includes vent 48 such that gas can be injected into dischargeline 12A during the brazing process, and gas can be vented out ofdischarge line 12A after the brazing process, during operation of thechiller, or during service or maintenance operations. Vent 48 comprisesany valve as is known in the art.

Thus, split discharge line 12A of the present invention is easilymanufactured and assembled and provides for the easy assembly of achiller system. In particular, the split discharge line accommodatesassembly variations in installed chiller systems that arise due toassembly variances or tolerance accumulation. For example, the splitdischarge line includes components that are formed from stock hardwaresuch that the discharge line is readily customizable. The splitdischarge line includes various assembly points such that theconfiguration thereof is readily adjustable. The split discharge linealso incorporates other system components, such as mufflers and valves,in a compact manner. Additionally, the split discharge line accommodatesoil separators having dual inlet openings and regulates refrigerant flowto improve oil separation. In other embodiments of the invention, thediameters and lengths of the various tubing are sized to assist inattenuating pulsations in the compressed refrigerant discharged fromcompressor 16. For example, the lengths and diameters of split lines 40Aand 40B and outlet lines 44A and 44B can be selected based on themagnitude of the wavelengths of the pulsations in the refrigerant toattenuate such pulsations, as is known in the art. The split dischargeline also minimizes pressure loss between a compressor and condenser ina vapor-compression system.

Although the present invention has been described with reference topreferred embodiments, workers skilled in the art will recognize thatchanges may be made in form and detail without departing from the spiritand scope of the invention.

1. A discharge pipe for connecting a compressor with a condenser in avapor-compression system, the discharge pipe comprising: an intakesegment connectable to a discharge port of the compressor in fluidcommunication therewith for receiving compressed refrigerant flowtherefrom; a muffler coupled in fluid communication to the intakesegment for attenuating pulsations within the compressed refrigerantflow; a splitter connected to an outlet of the muffler and configured todivide the compressed refrigerant flow into first and second branches; afirst discharge segment connected to the splitter to receive the firstbranch and configured to connect to the condenser at a first position;and a second discharge segment connected to the splitter to receive thesecond branch and configured to connect to the condenser at a secondlocation.
 2. The discharge pipe of claim 1 wherein the muffler isconfigured to dampen vibrations produced by the refrigerant flow.
 3. Thedischarge pipe of claim 1 wherein the first discharge segment and thesecond discharge segment are configured to enter the condenser atpositions near opposite distal ends of the condenser.
 4. The dischargepipe of claim 3 wherein the first discharge segment and the seconddischarge segment are configured to connect to an oil separator withinthe condenser.
 5. The discharge pipe of claim 4 wherein the splitter,the first discharge segment and the second discharge segment areconfigured to produce a decrease in velocity of the refrigerant flowfrom the intake segment to the discharge segments.
 6. The discharge pipeof claim 4 wherein the first discharge segment and the second dischargesegment have respective diameters and lengths configured to attenuatepulsations within the refrigerant.
 7. The discharge pipe of claim 1 andfurther comprising: a first stop-valve positioned in the first dischargepipe; and a second stop-valve positioned in the second discharge pipe.8. The discharge pipe of claim 1 wherein the discharge segments are eachcomprised of multiple segments having customizable assemblyorientations.
 9. The discharge pipe of claim 8 wherein the inlet portionand the splitter segment are comprised of steel and the first and seconddischarge segments are comprised of copper.
 10. The discharge pipe ofclaim 9 wherein the splitter segment further comprising a valve forventing gas into and out of the discharge pipe.
 11. The discharge pipeof claim 10 wherein the multiple segments are brazed together.
 12. Thedischarge pipe of claim 8 wherein: the intake segment comprises a firstelbow joint for turning the refrigerant flow ninety degrees; thesplitter segment includes a T-joint for turning the refrigerant flowninety degrees; and the first and second discharge pipes include secondand third elbow joints, respectively, for turning the refrigerant flowninety degrees.
 13. The discharge pipe of claim 1 wherein the first andsecond discharge segments include bends in the range of about twentyfive to about thirty five degrees.
 14. A vapor-compression systemcomprising: a compressor comprising: a mechanical compression system forcompressing a working fluid; a lubrication system for providing oil tothe mechanical compression system; and a discharge port for dispensingcompressed working fluid entrained with oil; a condenser mountedadjacent the compressor, the condenser comprising: a condenser shell; acondenser bundle of heat exchange tubes disposed within the condensershell; and an oil separator disposed within the condenser shell forextracting oil entrained from the compressed working fluid, the oilseparator having a first inlet and a second inlet; and a dischargeconduit for connecting the discharge port of the compressor with thefirst and second inlets of the oil separator within the condenser, thedischarge conduit comprising: an elbow joint for directing compressedworking fluid from the discharge port toward the condenser; a mufflerconnected to the elbow joint for attenuating pulsations within theworking fluid; a splitter connected to the muffler and configured todivide the compressed refrigerant flow into first and second branches;and first and second legs connected to the splitter to receive the firstand second branches, respectively, and configured to connect to thecondenser at the first and second inlets, respectively.
 15. Thevapor-compression system of claim 14 and further comprising: anevaporator mounted to the condenser adjacent the compressor, theevaporator comprising: an evaporator shell; and condenser bundle of heatexchange tubes disposed within the evaporator shell; first and secondbrackets for connecting the evaporator shell with the condenser shellsuch that the condenser, the evaporator and the compressor are linearlyarranged; and wherein there exists accumulated tolerance dimensions in adistance between the discharge port and each of the first and secondinlets.
 16. The vapor-compression system of claim 15 wherein the firstand second legs are each comprised of a plurality of segments toaccommodate the accumulated tolerance dimensions.
 17. Thevapor-compression system of claim 16 wherein the pluralities of segmentsare comprised of copper tubing components brazed together.
 18. Thevapor-compression system of claim 16 wherein: the first leg includes afirst valve disposed between the splitter and the first inlet; and thefirst leg includes a second valve disposed between the splitter and thefirst inlet.
 19. The vapor-compression system of claim 14 wherein thecompressor comprises a screw compressor.
 20. The vapor-compressionsystem of claim 14 wherein the first leg and the second leg produce adecrease in velocity of refrigerant flowing from the discharge port tothe oil separator.